US6257377B1 - Electromechanically actuatable brake - Google Patents

Electromechanically actuatable brake Download PDF

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Publication number
US6257377B1
US6257377B1 US09/319,961 US31996199A US6257377B1 US 6257377 B1 US6257377 B1 US 6257377B1 US 31996199 A US31996199 A US 31996199A US 6257377 B1 US6257377 B1 US 6257377B1
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United States
Prior art keywords
brake
bracing means
lining
spindle drive
spindle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US09/319,961
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English (en)
Inventor
Frank Schumann
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHUMANN, FRANK
Application granted granted Critical
Publication of US6257377B1 publication Critical patent/US6257377B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/06—Locking mechanisms, e.g. acting on actuators, on release mechanisms or on force transmission mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2129/00—Type of operation source for auxiliary mechanisms
    • F16D2129/06—Electric or magnetic
    • F16D2129/065—Permanent magnets

Definitions

  • the invention relates to an electromechanically actuatable brake.
  • one such electromechanically actuatable brake is known with a two-part actuating device, namely a first part for overcoming the air clearance and a second part for pressing a brake lining against a brake body.
  • Both parts of the actuating device have a separate spindle drive, drivable by its own electric actuating motor.
  • the two parts of the actuating device can be driven simultaneously or successively to execute a brake actuation, by putting the two motors into operation.
  • Both parts of the actuating device are joined together by a blocking bracing means embodied as a pair of levers.
  • the pair of levers is pivotably supported about a stationary shaft.
  • the first part of the actuating device engages the pair of levers with slight spacing from the shaft, while the second part of the actuating device engages the pair of levers with major spacing from the shaft. Because of this arrangement, the first part of the actuating device, which acts directly on the brake lining, is capable of rapidly overcoming the air clearance; via the pair of levers and the first part of the actuating device, the second part of the actuating device can generate a high contact-pressure force on the brake lining. Both motors of the actuating device can be equipped with a brake. Thus, unintended adjustment of the brake during braking operations can be avoided with a constant braking force while the motors are turned off.
  • the known brake is intended particularly for use in railroad vehicles. There the requisite installation space for the two parts of the actuating device and the relatively large-volume for the pair of levers is available in the known brake device. But because of its weight and volume, the brake would be unsuited to disposition in the bowl of a wheel rim of a road vehicle. Moreover, because of the two motors, the brake is expensive and requires increased expense for control. Thus, the bracing means is blocked only when, in successive drive of the two parts of the actuating device, the part serving to press the brake lining is not driven, or in other words only whenever only the air clearance is overcome. If both parts of the actuating device are driven simultaneously, conversely, the bracing means is not blocked.
  • the bracing means can be released by swiveling the pair of levers about the fixed shaft. Pivoting the pair of levers is done by driving the motor of the part of the actuating device used to press the brake lining. If one or both motors of the actuating device fail, problems can arise in releasing the actuating brake.
  • a brake is also known for pressing a brake lining against a rotating brake body (brake disk, brake disk or the like), which has an actuating device with a threaded roller drive, which is drivable by an electric motor. Both tightening and releasing the known brake are accomplished with the electric motor.
  • a preferably spiral restoring spring is provided in one embodiment of the known brake; this spring engages the actuating unit and drives the actuating unit, together with the electric motor, to rotate in the release direction so that the brake lining is lifted from the brake body.
  • This brake has the disadvantage that when brake pressure is built up, the force of the restoring spring must additionally be overcome, and the electric motor must therefore be dimensioned correspondingly larger and supplied with a higher current. In addition, there is a dynamic loss, and a loss of efficiency.
  • Another disadvantage is that to keep a built-up brake force constant, the electric motor must be supplied with such a high current that it keeps the brake lining pressed against the brake body with a constant contact pressure, counter to the force of the restoring spring, which entails thermal problems. Another factor is that the known brake cannot be used as a parking brake, because it releases when it has no current. Another disadvantage is that the brake cannot be released if the threaded roller drive is jammed.
  • Another disadvantage is that an air clearance, that is, a spacing between the brake lining and the brake body when the brake is released, increases with increasing wear of the brake linings.
  • an air clearance that is, a spacing between the brake lining and the brake body when the brake is released.
  • a positioning travel of the brake lining until the brake lining contacts the brake body becomes greater and accordingly it takes longer until the brake grabs.
  • the dynamic loss is additionally increased.
  • the force necessary to overcome the force of the restoring spring increases, because the restoring spring is deformed more markedly.
  • the energy that has to be brought to bear by the electric motor of the actuating device to deform the restoring spring is equivalent to the product of the deformation travel and deformation force; thus as the air clearance increases, this energy increases at least quadratically, which quite severely worsens the efficiency of the brake when the brake linings become worn.
  • the electromechanically actuatable brake of the invention as defined by the characteristics of claim 1 has a bracing means that is releasable by rotation and is blocked against rotation by an anti-jam device.
  • the bracing means can be embodied on the order of a bayonet mount, which can be released by turning the mount by a small angle and displacing the mount axially away from the brake body.
  • a bracing means that has a screw thread, which can be moved away from the brake body by turning the bracing means and is blocked against rotation by the anti-jam device.
  • a screw thread that extends over less than one full revolution can be adequate.
  • the actuating device is braced against the bracing means when the brake is actuated, or in other words for pressing the brake lining against the brake body.
  • the bracing means acts as a fixed abutment for the actuating device but otherwise has no function.
  • the brake is actuated and released with the actuating device.
  • the bracing means affects neither the actuating device itself nor its efficiency.
  • the rotation of the bracing means can also be done by means of a prestressed spring element, which rotates the bracing means in the release direction when the anti-jam device is released.
  • the bracing means moves away from the brake body, or if the bracing means is embodied like a bayonet mount, the bracing means is displaceable freely away from the brake body, so that the actuating device together with the brake lining is also released from the brake body; in other words, the bracing means acting as an abutment for the actuating device is removed or at least its distance from the brake body is increased.
  • the invention has the advantage that its bracing means neither affects the function of the actuating device nor worsens its efficiency.
  • the brake of the invention can also be used as a parking brake, which maintains braking moment without being supplied with current.
  • the brake of the invention has the advantage of optimally utilizing the energy stored in the brake because of the structural design of its releasable bracing means.
  • the screw thread thereof is designed for optimal reverse torque; that is, the tightening force of the brake, in the event of a malfunction, is automatically reduced to zero when the brake is released.
  • fewer structural components for releasing the brake in a malfunction are needed, which has advantages with respect to installation space, weight, costs, and power electronics.
  • FIGURE of the drawing is a section through a brake of the invention.
  • the brake of the invention shown in the drawing is embodied as a disk brake 10 with a so-called floating or sliding caliper 12 , in which two brake linings 14 are disposed, one on each side of a brake disk 16 rotatable between them.
  • the disk brake 10 has a spindle drive, specifically, because of its good efficiency, a threaded roller drive 18 .
  • a spindle drive has the advantage that an always-constant air clearance can be established between the brake linings 14 and the brake disk 16 , regardless of wear of the brake linings 14 . This has the advantage that a positioning distance and a positioning time until the brake linings 14 , upon actuation of the disk brake 10 , come to contact the brake disk 16 do not get any longer even when the brake linings 14 become worn.
  • the threaded roller drive 18 includes a nut 20 , which coaxially surrounds a spindle 22 .
  • threaded rollers 24 are distributed over the circumference, whose threads engage both the nut thread and the spindle thread.
  • the rollers 24 orbit the spindle 22 like the planet wheels of a planetary gear and cause an axial motion of the spindle 22 .
  • One of the two brake linings 14 is disposed, in a manner fixed against relative rotation, on one face end of the spindle 22 and can be pressed against one side of the brake disk 16 in order to bring a braking force to bear by driving the nut 20 to rotate.
  • the other one of the two brake linings 14 is pressed in the process, in a known manner, against the other side of the brake disk 16 by the reaction force of the brake caliper 12 .
  • the nut 20 of the threaded roller drive 18 is driven to rotate in the opposite direction.
  • the nut 20 For its rotational drive, the nut 20 has a polygonal profile in its outer circumference, onto which a polygonal cuff 26 whose inside has a complementary polygonal profile is thrust.
  • the polygonal profile can have a square cross section, whose corners are intersected by a concentric circle, as known from DIN 32712.
  • a polygonal profile is especially suitable for connecting the nut 20 of the threaded roller drive 18 to the polygonal cuff 26 in a manner fixed against relative rotation; these elements are intended to be longitudinally displaceable relative to one another when loaded with a torque.
  • the two polygonal profiles have a clearance fit from one another; that is, the nut 20 is axially displaceable relative to the polygonal cuff 26 and is connected to the polygonal cuff in a manner fixed against relative rotation.
  • the polygonal cuff 26 is supported rotatably in the floating caliper 12 by two ball bearings 28 .
  • Permanent magnets 34 are inserted into an outer circumference of the polygonal cuff 26 ; the polygonal cuff 26 forms a rotor of an electric actuating motor of the brake 10 of the invention.
  • a stator that has lamination packets 32 and stator windings on the permanent magnets 34 surrounds the polygonal cuff 26 forming the rotor.
  • the stator 32 , 34 is inserted solidly into the floating caliper 12 .
  • the nut 20 of the threaded roller drive 18 By turning on the actuating motor 26 , 30 , 32 , 34 , the nut 20 of the threaded roller drive 18 , which is connected in a manner fixed against relative rotation to the polygonal cuff 26 forming the rotor of the actuating motor, is set into rotation, and the spindle 26 is axially displaced thereby and the brake 10 of the invention is actuated or released, depending on the direction of the rotation, as described above.
  • the nut 20 of the spindle drive 18 is braced via a needle bearing 36 against a disk-like flange hub 38 , which is pressed in a manner that transmits both force and moment onto a tang 40 that is integral with a second spindle 42 .
  • the second spindle 42 is screwed into a female thread of a cap 44 secured onto the floating caliper 12 ; the cap forms the spindle nut for the second spindle 42 .
  • This spindle and spindle nut arrangement 42 , 44 forms a bracing means, which is releasable by rotation, for the nut 20 of the threaded roller drive 18 of the actuating device.
  • the bracing means 38 , 42 , 44 is free of anti-jamming because of the pitch of its screw thread and the diameter of its spindle 42 .
  • the brake 10 of the invention has an anti-jam device 46 , which blocks the bracing means 38 , 42 , 44 against rotating.
  • an electromagnetic spring pressure brake which is preferably closed when without current, or an indexable trip-free mechanism can be used.
  • the anti-jam device 46 includes a permanent magnet brake 48 with an armature disk 50 , which is disposed on a side of the flange hub 38 remote from the threaded roller drive 18 . Via bolts 52 inserted into the flange hub 38 , the flange hub 38 and the armature disk 50 are joined together in a manner fixed against relative rotation.
  • annular permanent magnet 54 which is mounted solidly on an inside of the cap 44 , attracts the armature disk 50 against a friction lining 56 in the form of an annular disk, which is inserted into the face end of the permanent magnet 54 toward the armature disk 50 .
  • the flange hub 38 forming the bracing means for the nut 20 of the threaded roller drive 18 is blocked against rotation; it forms an abutment against which the nut 20 of the threaded roller drive 18 is braced when the brake lining 14 is pressed against the brake disk 16 .
  • An electromagnet 58 is inserted into the annular permanent magnet 54 of the permanent magnet brake 48 .
  • the electromagnet 58 builds up a magnetic field that is oriented counter to the magnetic field of the permanent magnet 54 and virtually cancels the latter magnetic field out.
  • the armature disk 50 and together with it, the flange hub 38 forming the bracing means become freely rotatable; that is, the blocking of the bracing means is undone.
  • the electromagnet 58 is connected to a power supply that is independent of the power supply to the actuating motor 26 , 30 , 32 , 34 , so that release of the brake 10 will be assured even if the power supply of the actuating motor 26 , 30 , 32 , 34 fails.
  • the brake may have a prestressed spring element, in the form of a leaf-spiral spring 60 or torsion spring, which surrounds the second spindle 42 and engages it and braces it against the cap 44 .
  • This prestressed spiral spring 48 after the release of the permanent magnet brake 48 , rotates the second spindle 42 in such a way that the second spindle 42 moves together with the flange hub 38 away from the brake disk 16 .
  • the brake lining 14 is lifted away from the brake disk 16 .
  • the second spindle 42 need not be free of jamming.
  • the prestressed spring element furnishes the entire reverse torque for the releasable bracing means 38 , 42 . It compensates for fluctuations in reverse torque caused by fluctuations in the coefficient of friction, temperature factors, etc. Furthermore, it minimizes the reverse torque that holds the permanent magnet brake 48 closed, or in other words has a reinforcing effect.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
US09/319,961 1996-12-16 1997-10-01 Electromechanically actuatable brake Expired - Lifetime US6257377B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19652229A DE19652229A1 (de) 1996-12-16 1996-12-16 Elektromechanisch betätigbare Bremse
DE19652229 1996-12-16
PCT/DE1997/002258 WO1998027356A1 (de) 1996-12-16 1997-10-01 Elektromechanisch betätigbare bremse

Publications (1)

Publication Number Publication Date
US6257377B1 true US6257377B1 (en) 2001-07-10

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ID=7814829

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/319,961 Expired - Lifetime US6257377B1 (en) 1996-12-16 1997-10-01 Electromechanically actuatable brake

Country Status (5)

Country Link
US (1) US6257377B1 (de)
EP (1) EP0944781B1 (de)
JP (1) JP2001506348A (de)
DE (2) DE19652229A1 (de)
WO (1) WO1998027356A1 (de)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6374958B1 (en) * 1999-03-31 2002-04-23 Tokico Ltd. Motor-driven disk brake
US6412610B1 (en) * 1999-11-24 2002-07-02 Delphi Technologies, Inc. Electric brake caliper
US6554109B1 (en) * 1998-07-07 2003-04-29 Skf Engineering And Research Centre B.V. Actuator having a central support, and brake calliper comprising such actuator
US20030199356A1 (en) * 2002-04-19 2003-10-23 Biallas Jeffrey J. Electrically-actuated braking clutch for transmission
US20040104088A1 (en) * 2002-11-29 2004-06-03 Takuya Usui Motor-driven disk brake
US20040109916A1 (en) * 2002-12-03 2004-06-10 Mold-Masters Limited Hot runner co-injection nozzle
US6752249B1 (en) * 1999-09-23 2004-06-22 Continental Teves Ag & Co., Ohg Actuating unit for an electromechanically actuated disc brake
US20050189890A1 (en) * 2004-02-27 2005-09-01 Hitachi, Ltd. Control apparatus for electric motor of inverter system and control apparatus for electro mechanical brake
US20060054428A1 (en) * 2003-05-09 2006-03-16 Lucas Automotive Gmbh Vehicle brake and method for actuating a vehicle brake
EP1686281A1 (de) * 2005-01-26 2006-08-02 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Nachstellvorrichtung für eine Scheibenbremse
KR100659602B1 (ko) 2005-11-29 2006-12-20 주식회사 태성 브레이크 바이 와이어식 차량 제동장치 및 제동방법
US20080110704A1 (en) * 2005-01-13 2008-05-15 Tsugito Nakazeki Electric Direct-Acting Actuator and Electric Brake Device
US20080217121A1 (en) * 2005-07-29 2008-09-11 Chi-Thuan Cao Electromechanical Brake
US20090133975A1 (en) * 2005-09-27 2009-05-28 Leo Gilles Vehicle Brake, In Particular Caliper Brake
US20090194385A1 (en) * 2006-07-07 2009-08-06 Chi-Thuan Cao Positive-Fit Freewheel Mechanism That Can Be Electromechanically Actuated, Electromechanical Brake With A Freewheel Mechanism Of This Type For A Motor Vehicle and Method For Adjusting The Play In A Brake Of This Type
US20110291503A1 (en) * 2009-02-19 2011-12-01 Zf Friedrichshafen Ag Electromechanical arrangement for driving and/or braking a shaft
US20130264153A1 (en) * 2010-12-17 2013-10-10 Continental Teves Ag & Co. Ohg Electromechanically Actuatable Brake and Method for Operating an Electromechanically Actuatable Brake
US20160207613A1 (en) * 2015-01-15 2016-07-21 Goodrich Corporation Bi-stable voice coil park brake
US9527584B2 (en) * 2015-01-16 2016-12-27 Goodrich Corporation Electromechanically actuated brake with supplemental back drive
EP3392516A1 (de) * 2013-07-02 2018-10-24 Goodrich Corporation Elektromotorischer stellantrieb
US20210356008A1 (en) * 2018-09-18 2021-11-18 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Brake Assembly and Method for Controlling a Brake Assembly
CN114922918A (zh) * 2021-02-11 2022-08-19 维美德技术有限公司 纤维幅材机、特别是分切复卷机的惰辊的制动器

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DE19858764C2 (de) * 1998-12-18 2000-11-02 Siemens Ag Elektromechanische Kraftfahrzeug-Bremsvorrichtung
DE19859325A1 (de) * 1998-12-22 2000-06-29 Bosch Gmbh Robert Verfahren zum Betrieb einer elektromechanischen Radbremsvorrichtung
DE19941936C2 (de) * 1999-09-03 2001-07-26 Daimler Chrysler Ag Elektrischer Bremsaktor
DE19953805C1 (de) * 1999-11-09 2001-06-21 Daimler Chrysler Ag Kombinierter Betriebs- und Federspeicherbremszylinder und Bremseinrichtung für Nutzfahrzeuge
DE19955080A1 (de) * 1999-11-15 2001-05-17 Continental Teves Ag & Co Ohg Betätigungseinheit für eine elektromechanisch betätigbare Feststellbremse für Kraftfahrzeuge
DE10255192B4 (de) * 2002-11-27 2015-03-19 Robert Bosch Gmbh Elektromechanische Bremse
DE502005001721D1 (de) † 2004-05-10 2007-11-29 Ovalo Gmbh Vorrichtung zum überlagern von lenkbewegungen für eine lenkkrafthilfe sowie verfahren zum betreiben der vorrichtung
DE102011084190B4 (de) 2011-10-10 2022-12-22 Continental Automotive Technologies GmbH Elektrisch betätigbare Kraftfahrzeugbremse mit einer Feststellbremsvorrichtung
DE102012103506A1 (de) * 2012-04-20 2013-10-24 Ipgate Ag Innenläufer-Motor
KR102020530B1 (ko) 2012-04-20 2019-09-10 이페게이트 아게 축방향 구동부의 베어링 배열

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JP2973707B2 (ja) * 1992-05-15 1999-11-08 トヨタ自動車株式会社 ディスクブレーキ
DE19511287B4 (de) 1994-07-21 2004-05-06 Continental Teves Ag & Co. Ohg Elektromechanische betätigbare Scheibenbremse
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GB2190441A (en) 1986-05-17 1987-11-18 Westinghouse Brake & Signal Force actuator

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6554109B1 (en) * 1998-07-07 2003-04-29 Skf Engineering And Research Centre B.V. Actuator having a central support, and brake calliper comprising such actuator
US6374958B1 (en) * 1999-03-31 2002-04-23 Tokico Ltd. Motor-driven disk brake
US6752249B1 (en) * 1999-09-23 2004-06-22 Continental Teves Ag & Co., Ohg Actuating unit for an electromechanically actuated disc brake
US6412610B1 (en) * 1999-11-24 2002-07-02 Delphi Technologies, Inc. Electric brake caliper
US20030199356A1 (en) * 2002-04-19 2003-10-23 Biallas Jeffrey J. Electrically-actuated braking clutch for transmission
US6699153B2 (en) * 2002-04-19 2004-03-02 General Motors Corporation Electrically-actuated braking clutch for transmission
DE10355660B4 (de) * 2002-11-29 2015-06-25 Hitachi, Ltd. Motorbetriebene Scheibenbremse
US6959791B2 (en) * 2002-11-29 2005-11-01 Kabushiki Kaisha Hitachi Seisakusho Motor-driven disk brake
US20040104088A1 (en) * 2002-11-29 2004-06-03 Takuya Usui Motor-driven disk brake
US20040109916A1 (en) * 2002-12-03 2004-06-10 Mold-Masters Limited Hot runner co-injection nozzle
US7316300B2 (en) * 2003-05-09 2008-01-08 Lucas Automotive Gmbh Vehicle brake and method for actuating a vehicle brake
US20060054428A1 (en) * 2003-05-09 2006-03-16 Lucas Automotive Gmbh Vehicle brake and method for actuating a vehicle brake
US20050189890A1 (en) * 2004-02-27 2005-09-01 Hitachi, Ltd. Control apparatus for electric motor of inverter system and control apparatus for electro mechanical brake
US20070029953A1 (en) * 2004-02-27 2007-02-08 Hitachi, Ltd. Control apparatus for electric motor of inverter system and control apparatus for electro mechanical brake
US7215090B2 (en) * 2004-02-27 2007-05-08 Hitachi, Ltd. Control apparatus for electric motor of inverter system and control apparatus for electro mechanical brake
US7285927B2 (en) 2004-02-27 2007-10-23 Hitachi, Ltd. Control apparatus for electric motor of inverter system and control apparatus for electro mechanical brake
US7810616B2 (en) * 2005-01-13 2010-10-12 Ntn Corporation Electric direct-acting actuator and electric brake device
US20080110704A1 (en) * 2005-01-13 2008-05-15 Tsugito Nakazeki Electric Direct-Acting Actuator and Electric Brake Device
EP1686281A1 (de) * 2005-01-26 2006-08-02 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Nachstellvorrichtung für eine Scheibenbremse
US20080217121A1 (en) * 2005-07-29 2008-09-11 Chi-Thuan Cao Electromechanical Brake
US8020675B2 (en) 2005-07-29 2011-09-20 Robert Bosch Gmbh Electromechanical brake
CN101233031B (zh) * 2005-07-29 2012-07-18 罗伯特·博世有限公司 机电制动器
US20090133975A1 (en) * 2005-09-27 2009-05-28 Leo Gilles Vehicle Brake, In Particular Caliper Brake
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US8618705B2 (en) * 2009-02-19 2013-12-31 Zf Friedrichshafen Ag Electromechanical arrangement for driving and/or braking a shaft
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EP0944781B1 (de) 2002-03-27
EP0944781A1 (de) 1999-09-29
WO1998027356A1 (de) 1998-06-25
DE59706805D1 (de) 2002-05-02
JP2001506348A (ja) 2001-05-15
DE19652229A1 (de) 1998-06-18

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